Flow Conditioner and Method for Optimization

ABSTRACT

A flow conditioner for a circular pipe having an axis. The flow conditioner includes a plate having a face to be disposed in the circular pipe with the face of the plate perpendicular to the axis of the pipe. The plate has a central circular passage area through which fluid flows surrounded by two or more concentric arrays of segmented annular passages for fluid flow defined by separating and subdividing ligaments, with at least one subdividing ligament having a width different than a width of a second subdividing ligament. Alternatively, or in addition, there is at least one array of annular passages having a radial width different than a radial width of a second array of annular passages and at least one subdividing ligament having a width different than a width of a second subdividing ligament. A method of producing an optimized geometry of flow conditioner for a circular pipe having an axis.

FIELD OF THE INVENTION

The present invention is related to a flow conditioner for flowregarding a flow metering device. (As used herein, references to the“present invention” or “invention” relate to exemplary embodiments andnot necessarily to every embodiment encompassed by the appended claims.)More specifically, the present invention is related to a flowconditioner for a flow metering device where the conditioner has acentral circular passage area through which fluid flows surrounded bytwo or more concentric arrays of segmented annular passages for fluidflow defined by separating and subdividing ligaments.

BACKGROUND OF THE INVENTION

This section is intended to introduce the reader to various aspects ofthe art that may be related to various aspects of the present invention.The following discussion is intended to provide information tofacilitate a better understanding of the present invention. Accordingly,it should be understood that statements in the following discussion areto be read in this light, and not as admissions of prior art.

In the field of flow measurement, it is often necessary to condition theflow upstream of a flow metering device in order that the flow meterwill register flow with a minimal error. Bends, valves, filters andother forms of pipeline component distort the flow velocity profile andby changing the flow direction introduce non-axial velocity componentsor ‘swirl’ in the flow stream. It is well known that the calibration orflow coefficient of certain types of flow meter is affected bydistortions of the profile and/or by the presence of swirl. Flowconditioners have been employed for many years to partially rectifydistorted and swirling flows upstream of flow meters. The variousdevices deployed to date differ in design with resulting differences inperformance in terms of their ability to rectify flow versus thepermanent pressure loss that they impose. Most conditioners have asingle specified geometry or a constrained set of design parameters andcannot easily be adapted to suit the requirements of a particularsituation. The invention described here aims to overcome these and otherlimitations of existing conditioners.

Flow conditioners have been used for many years to attempt with the aimof rectifying incoming flow conditions and improving flow meteraccuracy. By far the most common type of flow conditioner has been a‘flow straightener’ of either the vane type or in the form of a tubebundle assembly. Flow straighteners essentially divide the flow into anumber of passages that are long and straight in parallel with the axisof the pipe. The aim is that any rotational component of velocity isreduced or eliminated when the flow exits the conditioner.

The tube bundle is the most commonly employed form of flow straightener,having been standardized to some degree, and is essentially an assemblyof tubes, typically between 7 and 55 in total, arranged either in ahexagonal or circular geometry, as illustrated in FIGS. 1 a and 1 b. Atube bundle using 19 tubes of equal size arranged in a circular geometryis included in the International Standard for differential pressure flowmeters, 1505167. Tube bundles are typically made to be between two andthree pipe diameters in length, with the result that the tubes may be 20to 30 tube diameters long, though studies have shown that in terms oflimiting swirl, a much shorter length of bundle can still be effective.

A recognized deficiency of the tube bundle design of flow conditioner isthat while it is effective at removing swirl, the emerging axialvelocity profile does not tend to be fully developed, that is itgenerally tends to be flatter than the profile that would be founddownstream of a long straight length of pipe at the Reynolds number ofinterest. In order to try to overcome this limitation, Stuart developeda tube bundle flow conditioner where the tube diameters used within thebundle were varied in order to produce a velocity profile shape closerto the desired fully developed profile. A disadvantage of thisconditioner design in terms of manufacturing, which also applies to mosttube bundle designs, is that when pipe diameter is varied, the requiredtube diameters may not be readily available in standard sizes of tubing.The main advantage of tube bundles is that they have relatively lowpermanent pressure loss, having a loss coefficient for fully turbulentflow in the range of 0.65 to 1.2.

A further disadvantage of the tube bundle is its variable design andquality. If not constructed to the ISO standard, the potentialvariations in number and size of tubes are almost endless, making itdifficult to predict performance or relate experience from one design oftube bundle to another. Furthermore, variable manufacturing qualitymeans that the tube alignment may vary, and in some cases, for exampleif the bundle becomes twisted during manufacture, the bundle can producea swirling flow.

The need to shape the axial velocity profile as well as remove swirl wasprobably first addressed properly in the design of the Zanker flowconditioner. The Zanker conditioner comprises a thin plate with holesdesigned to produce a graded resistance to flow combined with a vanetype straightener attached to the downstream side of the plate. In termsof the flow profile produced and level of swirl reduction achieved bythis conditioner, it is recognized as being very effective. However, itis somewhat difficult to manufacture and has a high pressure losscoefficient of greater than 5.

More commonly used today are thick-plate type conditioners. In thesedesigns a graded resistance to flow is achieved by means of makingcircular passages in a fairly thick plate. By varying the number,spacing and/or size of the circular passages, the desired gradedresistance is achieved. Examples of this type of conditioner includethose by Laws (most common in the Nova/CPA 50E variant), Spearman, andGallagher, in addition to the thick plate version of the Zankerconditioner, where the thicker plate negates the requirement for thedownstream vane-type straightener. Common thick-plate conditioners areillustrated in FIGS. 2 a-2 d.

These thick-plate conditioners with circular passages are considered thecurrent state-of-the-art but still have certain deficiencies. Pressureloss coefficients are typically in the range of 2 to 5, greater thanthat available with a tube bundle. Attempts to produce plates of higherporosity and hence lower pressure loss have generally resulted in areduction in flow conditioning performance.

Optimization of the design of a thick-plate conditioner with circularpassages is complicated by particular issues associated with the chosencircular hole geometry. An irregular numbers of holes and the circularshape of the passages result in a complex ‘water-shed’ between adjacentrings of holes, and hence makes the calculation of the effectiveporosity difficult as the water-shed defines the blockage areaassociated with each hole. Optimization is further complicated in caseswhere the circular passage size is varied, as for a given thickness ofplate as this results in variation of both the porosity and the ratio ofthe length of the passage to its hydraulic diameter. As a consequence,the steps that should be taken to optimize a conditioner with circularpassages are not obvious, as when changes are made the shape of thewater shed varies as well as the porosity and the hydraulic diameter.

A particular advantage of the thick-plate conditioner is that themanufacture and geometric scaling to different sizes of pipe can beachieved very easily, which overcomes the manufacturing and qualitylimitations associated with the tube bundle type of conditioner.

As mentioned previously, the effectiveness of thick-plate conditionershas been found to diminish when the porosity is increased too much, withthe result that most thick-plate conditioners in use today have porosityin the region of 50%. When porosity has been increased, theinvestigators have not tended to increase plate thickness to compensatefor the reduction in l/d, which may partly explain the diminishedperformance. This has led some designers to add straightening vanes tothe conditioner or to employ two stages of conditioning, the first beinga straightening vane and the second a graded thick-plate conditioner.

Some types of flow meter are more affected by the condition of theincoming flow field than others. In the case of multi-path ultrasonicflow meters, it is often the case that if swirl is removed effectivelythen the meter will be able to perform with high accuracy in a varietyof different installation conditions. Therefore, it is common for tubebundles to be used with ultrasonic meters, owing to their lower pressureloss characteristics. However, this does not offset three of thedisadvantages of tube bundles: first, that they alter the axial velocityprofile in an adverse way; secondly the fact that they are generallymanufactured to be between 2 and 3 diameters long, and thirdly themanufacturing issues mentioned above that can result in poor qualityconditioners. Therefore, it is one purpose of the invention describedhere to be able to produce a low pressure loss flow conditioner for usewith ultrasonic and other types of flow meters. In addition to having alow permanent pressure loss, the conditioner should be easy tomanufacture in a reproducible way and it should be possible to vary thedesign parameters in order to obtain a desirable shape of axial velocityprofile.

BRIEF SUMMARY OF THE INVENTION

The flow conditioner of the current invention is based on an arrangementof segmented annular passages, arranged symmetrically around thecenter-line of a circular conduit. The choice of segmented annularpassages allows the cross-sectional area of the pipe to be divided intoa predetermined number of annular rings with the width and separation ofthe passages to be freely varied in both radial and tangentialdirections, to obtain a desired value of hydraulic diameter and porosityin each ring. Combined with control over the length of the passages viaselecting the thickness of the conditioner, this arrangement ofsegmented annular passages can be optimized to produce a conditionerwhich will retard swirl and have a desired radial distribution ofresistance, in combination with a specified overall pressure loss.

BRIEF DESCRIPTION OF THE SEVERAL VIEWS OF THE DRAWING

In the accompanying drawings, the preferred embodiment of the inventionand preferred methods of practicing the invention are illustrated inwhich:

FIGS. 1 a and 1 b show two typical arrangements of 19-tube tube bundleconditioners.

FIGS. 2 a-2 d show typical thick plate conditioner geometries.

FIG. 3 is an illustration of a complicated water-shed geometry betweenthe outer and middle rings when circular passages are used.

FIGS. 4 a and 4 b show a segmented annular geometry with circularcentral channel (three annular rings).

FIG. 5 a shows a segmented annular geometry with segmented centralchannel (two annular rings).

FIG. 5 b shows a segmented annular geometry with alternative means ofsubdivision.

FIG. 5 c is an illustration of example alternative forms of subdividingligament geometry.

FIG. 6 a is a graph showing convergence of the design towards thedesired velocity profile.

FIG. 6 b is a graph showing convergence of the design in terms of thehydraulic diameter of the passages.

FIG. 7 is an illustration of the design resulting from the optimizationexample.

FIG. 8 is a simplified flow chart illustrating the optimization process.

FIGS. 9 a, 9 b and 9 c show a resultant geometry including roundedinternal corners and flange.

FIG. 10 a shows meter factor versus Reynolds number for meter A instraight pipe and downstream of bends with no flow conditioner.

FIG. 10 b shows meter factor versus Reynolds number for meter B instraight pipe and downstream of bends with no flow conditioner.

FIG. 11 a shows meter factor versus Reynolds number for meter A instraight pipe and downstream of bends with the 4D-Lawsconditioner-10D-Meter arrangement.

FIG. 11 b shows meter factor versus Reynolds number for meter B instraight pipe and downstream of bends with the 4D-Lawsconditioner-10D-Meter arrangement

FIG. 12 a shows meter factor versus Reynolds number for meter A instraight pipe and downstream of bends with the 4D-Prototypeconditioner-10D-Meter arrangement.

FIG. 12 b shows meter factor versus Reynolds number for meter B instraight pipe and downstream of bends with the 4D-Prototypeconditioner-10D-Meter arrangement.

FIG. 13 shows swirl measured using the 8-path ultrasonic meter instraight pipe and 10D downstream of bends with no flow conditioning.

FIG. 14 shows swirl measured using the 8-path ultrasonic meter instraight pipe and downstream of bends with the 4D-conditioner-10D-Meterarrangement, for both the Laws type conditioner and the new prototype.

FIG. 15 shows a representation of the system of the present invention.

DETAILED DESCRIPTION OF THE INVENTION

Referring now to the drawings wherein like reference numerals refer tosimilar or identical parts throughout the several views, and morespecifically to FIGS. 4 a and 4 b thereof, there is shown a flowconditioner 10 for a circular pipe 12 having an axis 14. The flowconditioner 10 comprises a plate 16 having a face 18 to be disposed inthe circular pipe 12 with the face 18 of the plate 16 perpendicular tothe axis 14 of the pipe 12. The plate 16 has a central circular passagearea 20 through which fluid flows surrounded by two or more concentricarrays of segmented annular passages 22 for fluid flow defined byseparating and subdividing ligaments 24, with at least one array 26 ofannular passages 22 having a radial width different than a radial widthof a second array 28 of annular passages 22.

With reference to FIGS. 5 a-5 c, 7, 9 a and 9 b, the plate 16 may haveat least one subdividing ligament 30 having a width different than awidth of a second subdividing ligament 32. The central circular channelmay be subdivided into 2 or more separate passages 34. The subdivisioninto segmented annular passages 22 may be achieved by means of ligaments24 aligned along a radius of the circular geometry of the conditioner.The subdivision into segmented annular passages 22 may be achieved withligaments 24 that are aligned at an angle relative to a radius of thecircular geometry of the conditioner. The sides of each subdividingligament may be straight and parallel.

The sides of each subdividing ligament may be curved. The sides of eachsubdividing ligament may be non-parallel. The internal corners 40 of thesegmented annular passages 22 may be rounded. The upstream edges 36 ofthe passages may be chamfered or rounded. The downstream edges 38 of thepassages may be chamfered or rounded. All passages may have asubstantially equal hydraulic diameter. The ratio of the length of thepassages to their hydraulic diameter may be greater than 1.

The ligaments 24 that subdivide the annular passages 22 may getprogressively thicker at distances that are further from the center ofthe pipe 12, in order to obtain an approximation of a fully-developedflow profile.

The present invention pertains to a flow conditioner 10 for a circularpipe 12 having an axis 14. The flow conditioner 10 comprises a plate 16having a face 18 to be disposed in the circular pipe 12 with the face 18of the plate 16 perpendicular to the axis 14 of the pipe 12. The plate16 has a central circular passage area 20 through which fluid flowssurrounded by two or more concentric arrays of segmented annularpassages 22 for fluid flow defined by separating and subdividingligaments 24, with at least one subdividing ligament 30 having a widthdifferent than a width of a second subdividing ligament 32.

The present invention pertains to a flow conditioner 10 for a circularpipe 12 having an axis 14. The flow conditioner 10 comprises a plate 16having a face 18 to be disposed in the circular pipe 12 with the face 18of the plate 16 perpendicular to the axis 14 of the pipe 12. The plate16 has a central circular passage area 20 through which fluid flowssurrounded by two or more concentric arrays of segmented annularpassages 22 for fluid flow defined by separating and subdividingligaments 24, with at least one array 26 of annular passages 22 having aradial width different than a radial width of a second array 28 ofannular passages 22 and at least one subdividing ligament 30 having awidth different than a width of a second subdividing ligament 32.

The present invention pertains to a method of producing an optimizedgeometry of flow conditioner 10 for a circular pipe 12 having an axis14. The method comprises the steps of storing a desired value for apressure loss coefficient of the conditioner in non-transitory memory.There is the step of storing a shape of velocity profile desired in thememory. There is the step of setting manufacturing goals. There is thestep of storing a number of annular rings to be used in the conditionerto subdivide the pipe 12 cross-section in the memory. There is the stepof storing a number of subdivisions for each annular ring and for acentral circular passage area 20 of the conditioner in the memory. Thereis the step of setting a width of each annular ring to an initial valuein the memory. There is the step of setting a width of circularligaments 24 of the conditioner to an initial value in the memory. Thereis the step of setting a width of subdividing ligaments 24 of theconditioner to an initial value in the memory. There is the step ofcalculating a hydraulic diameter of each of the passages of theconditioner with a computer from information stored in the memory insteps a-g, the computer in communication with the memory. There is thestep of setting a thickness of the conditioner plate 16 to a value basedon a desired ratio of passage length to hydraulic diameter in thememory. There is the step of determining resistance and flowcharacteristics of the conditioner geometry with the computer based onsteps a-g. There is the step of adjusting the geometry iteratively withthe computer until the specified goals are achieved.

There may be the step of setting a pressure loss coefficient of lessthan 2 in the memory. There may be the step of the step of entering intothe memory a target flow profile based on fully developed flowconditions. There may be the step of entering into the memory a flatvelocity profile. There may be the step of entering into the memory aparabolic profile. There may be the step of entering into the memory avelocity profile representing fully developed turbulent flow. There maybe the step of including the step of setting a constraint that allpassages have a minimum dimension greater than 0.1 D in the memory.

There may be the step of setting a constraint that all ligaments 24 havea width of greater than 0.01 D in the memory. There may be the step ofsetting a constraint that all corners have a minimum radius of 0.01 D inthe memory. There may be the step of setting a constraint that allpassages have an essentially equal hydraulic diameter in the memory.There may be the step of setting a constraint that the minimum ratio ofthe length of the passages to their hydraulic diameter is greater than 1in the memory.

There may be the step of setting the number of annular rings to between2 and 12 in the memory. There may be the step of limiting the totalnumber of passages to 0.5 times the square of the number of rings in thememory. The adjusting step may include the step of adjusting the radialwidth of the segmented annular passages 22. The adjusting step mayinclude the step of adjusting the radial width of the subdividingligaments 24. The adjusting step may include the step of adjusting thewidth of the circular ligaments 24. The adjusting step may include thestep of adjusting the number of subdivisions in each annular area. Theadjusting step may include the step of adjusting the number of annularrings.

FIG. 15 shows a system 46 for measuring fluid flow in a pipe. The systemcomprises a conditioner 10 disposed in the pipe. The system comprisesultrasonic transducers 44 in communication with the fluid in the pipe.The system 46 comprises an ultrasonic flow meter 42 in communicationwith the pipe which determines the fluid flow from ultrasonic signalstransmitted and received by the transducers. An example of a flow meterwith ultrasonic transducers for fluid flow measurement that may be usedis available for purchase from Cameron International Corporation, havingmodel name Caldon LEFM 240Ci. Such a flowmeter 42 is designed togenerate and receive electronic signals from the transducers and toprocess the signals in order to compute information related to the fluidflow rate through the pipe.

In the operation of the invention, the conditioner described here isbased on dividing the cross-sectional area of a circular pipe 12 intoannular areas centered on the pipe 12 centerline, as illustrated inFIGS. 4 a and 4 b. Circular ligaments 99 separate these annular areasfrom one another and subdividing ligaments 24 partition each area intotwo or more segmented annular passages 22 through which the fluid canflow. The number and width or circular ligaments 24 combined with thenumber and width of subdividing ligaments 24 determines the overallporosity of the conditioner. Furthermore, by varying the number ofsubdividing ligaments 24, or the thickness of these ligaments 24 fromone area relative to another, the hydraulic diameter, d, and porositycan be varied, and hence the flow resistance can be graded to producethe desired flow characteristics.

The outer segmented-annular ring of passages can have an outer boundingwall included in the design of the conditioning element, or can be openat the outer circumference such that the inside wall of the pipe 12forms in the outer wall of each of those passages.

A benefit of use of a segmented annular geometry over circular passagesis easily explained by reducing one of the problems of circular holesdown to a simple example. Consider a conditioner with 19 circularpassages of equal size arranged in a hexagonal pattern. The maximum sizethat these passages can be before they merge together is one fifth ofthe inner diameter of the pipe 12. Therefore the maximum free area wouldbe approximately 76% of the pipe 12 area. With segmented annularpassages 22 the free area in any portion of the conditioner can belarger than this limit, whilst still having sufficient ligament widthfor mechanical strength of the conditioner.

In the preferred embodiment of this invention, the length, l, of eachsegmented annular passage is equal to the others and to the thickness ofthe plate 16, though variations with different passage lengths can alsobe conceived by changing the plate 16 thickness associated with eachring. It is however, important to consider the overall length of thepassages and their hydraulic characteristics. Passages that are tooshort in length will be ineffective at preventing the passage of swirl,whereas passages that are too long may increase the pressure loss orunnecessarily increase the size of the conditioner, with consequencesfor manufacturing. Furthermore if the ratio of the length of the passageto its hydraulic diameter differs from one set of holes to another, thenthe characteristics of the flow through the holes may differsignificantly as a function of the pipe 12 Reynolds number.

For passages that have a very short length to hydraulic diameter ratio(l/d), swirl will pass easily, and after the flow separates at theentrance to the passage, it will not reattach inside the passage (thiscan be termed fully separated flow). For passages of intermediate l/d,swirl may still pass, and the flow may or may not reattach inside thepassage depending on the flow conditions prevailing (this can be termedmarginally separated/attached flow). For passages of relatively longl/d, swirl will be suppressed and the separated flow at the entrance tothe passage will re-attach (this can be termed fully reattached flow).In terms of the pressure loss for flow through a passage between twosections of pipe 12 it can be shown that the pressure loss is greatestfor fully separated flow, and reduces to a minimum once the flow isfully reattached. Beyond the minimum pressure loss point the pressureloss will increase again owing to increased frictional losses in thepassages of the conditioner. Therefore it is possible to optimize a flowconditioner 10 in terms of the length to hydraulic diameter ratio.

For the common thick-plate 16 conditioners available today that usecircular passages, the thickness of the plate 16 is constant andnormally in the range of 0.12 to 0.15 relative to the pipe 12 diameter.The hole diameters are typically in the range of 0.1 to 0.19 relative tothe pipe 12 diameter, with resulting l/d values in the range of 0.63 to1.5. The range of l/d corresponding to marginally separated/attachedflow is typically between 0.5 and 1. In the likes of the Laws, Gallagherand Spearman plates, different values of passage diameter are used ineach conditioner, with the result that under certain flow conditionssome passages may have separated flow whereas others may have reattachedflow.

It is desirable to avoid the possibility of having both separated andreattached flow conditions occurring in different passages of the sameconditioner at the same time. One solution to this would be to increaseplate 16 thickness until fully reattached conditions occur in largest ofthe passages. However, when this is done the pressure loss coefficientwould then increase undesirably in the passages of smaller hydraulicdiameter. It is therefore attractive to be able to produce a conditionerdesign where the value of hydraulic diameter of all passages is thesame. When the hydraulic diameters of each passage are the same, thenwith a conditioner of constant thickness the values of l/d will also bethe same, and consequently the frictional component of pressure lossthrough the hole will also be the same. For circular passages, thehydraulic diameter is simply equal to the diameter, and therefore forlid to be constant the passages should all have the same diameter, whichimposes unwanted restrictions on the geometric arrangement of the holesin terms of producing the desired graded resistance. For segmentedannular passages 22, the hydraulic diameter is equal to four times thecross-sectional area divided by the perimeter. Therefore the hydraulicdiameter is a function not only of the cross-sectional area of thepassage, but also the aspect ratio of the passage. This provides greaterflexibility in design when it is desirable to vary or optimize theconditioner design in terms of both porosity and hydraulic diameter.

The conditioner of the current invention can be manufactured from avariety of materials by a method chosen to suit the materials ofconstruction. For conditioners that are to be used in small pipes ismost likely that the conditioner would be manufactured from a solid partmade of metal or plastic with the passages cut into the material usingmachine tools. Techniques such as water-jet cutting may be appropriatefor some materials up to a certain thickness or conventional drillingand milling techniques can be employed. For larger pipes, it isconceivable that the conditioner would be assembled by means such asusing pipe sections of different diameters for the circular ligaments99, and joining these to one another using subdividing ligaments 24 cutfrom sheet metal of a given thickness. This possibility highlights anadvantage of the current invention, in that the number, thickness anddiameter of the circular ligaments 99 could be selected from standardsizes of pipe. With the dimensions of the circular ligaments 99 fixed,the number and thickness of the subdividing ligaments 24 can then beselected in order to produce the desired porosity for each ring. In thedesign process the number of rings and number of subdividing ligaments24 can be constrained in order to produce an appropriate balance betweenmaterial and manufacturing cost.

The conditioner can be designed either to fit fully inside a pipesection with some means of securing it in place, or it can be designedto fit between pipe flanges. For increased mechanical strength, thesegmented annular passages 22 can be designed with rounded internalcorners 40. To reduce pressure loss without reducing the thickness ofthe circular 99 and subdividing ligaments 24 beyond a certain designvalue, inlets and/or outlets of the passages can be chamfered tostreamline the design and reduce flow separation.

In the center of the conditioner there will normally be a singularcircular passage but alternatively this could also be segmented to formtwo or more separate central passages as illustrated in FIGS. 5 a-5 cand FIGS. 6 a and 6 b.

In terms of practical preference, the conditioner would be installed asa single unit. However, two or more units could be installed in serieswith some separation in between in order to perform more effective flowconditioning. In terms of conditioning performance versus overallpressure loss, this may be preferable to using a single unit.

The design of a particular conditioner geometry according to the currentinvention begins with defining the required characteristics of theconditioner in terms of overall pressure loss and desired axial flowprofile shape. At this stage any other constraints or requirements canbe added such as the overall thickness of the plate 16, the minimumlength to hydraulic diameter ratio, the minimum width of circular 99 andsubdividing 24 ligaments, the minimum radius of the inside cornersand/or a specification that all passages have the same hydraulicdiameter. Next the general characteristics of the conditioner areconsidered in terms of the approximate total number and size of thepassages. Once the number of annular rings and the number of segmentsper ring has been determined, values are chosen to produce an initialdesign and then the optimization of the conditioner can begin (orindeed, it is also conceivable that the optimization process couldinclude varying the number of rings and segments per ring).

The thickness of the circular ligaments 99 between annular rings and thethickness of the subdividing ligaments 24 are set to initial valueschosen from a practical perspective. The radial width of the segmentedannular passages 22 is set to initial values (for example approximatelyequal) such that the total radial width of the passages plus thecircular ligaments 99 sums to the diameter of the conditioner. Thethickness of the plate 16 is set to an initial value.

The porosity, hydraulic diameter are then calculated for each ring.This, in addition to knowledge of the thickness of the conditioner,allows the pressure loss coefficient and relative velocity to beestimated for each segmented annular ring. In practice this can beachieved using semi-empirical pressure loss models that relate theseterms, such as those described by “I E Idelchik, Handbook of HydraulicResistance, 3^(rd) Edition, Jaico Publishing House, 2005”, incorporatedby reference herein. Alternatively, the profile and pressure losscharacteristics can be determined by means of computational fluiddynamics or by experimental testing. The geometry is then iterativelyadjusted until the desired velocity profile and other optimalcharacteristics are achieved.

Some trial and error may be required in terms of the starting conditionsand constraints in order to obtain convergence and produce a solutionthat has the required characteristics.

This process can now be illustrated by means of an example in which itis desired to produce a conditioner with a low pressure loss coefficientof 0.5, and with each passage having the same hydraulic diameter.

Common thick-plate type conditioners have between 25 and 32 circularpassages, with the outer holes typically being sized at approximately10% of the pipe diameter. Therefore for a conditioner design with abroadly similar number and size of passages one can start by dividingthe pipe 12 into a central circular passage and three annular rings, theradial width of each ring being less than 14% of the diameter. Thenusing radial subdividing ligaments 24, and taking into consideration adesire for symmetry, one can partition the inner annulus into sixsegments, and each of the outer annuli into 12 segments, resulting in 31passages in total. The thickness of the circular 99 and subdividingligaments 24 can be set to an arbitrary value to start, say 1% of thepipe 12 diameter. In this example it is started with circular 99 andsubdividing 24 ligaments of 0.01 D, and a width of 0.12 D for each ofthe annular sections, with the result that the starting diameter of thecentral circular passage is 0.2 D (given the constraint that the outerwall and circular ligaments 99 plus the width of the passages should sumto equal the pipe 12 diameter).

At this point, the hydraulic diameter of the largest passage is 0.2 D.Given that it is desirable to target an lid value of greater than 1, aplate 16 thickness of 0.2 D is selected at this stage, which shouldensure that this requirement is met, and can of course be adjusted aspart of the optimization process.

In the case of a single central passage, its porosity is determined byits diameter and by the thickness of the circular ligament thatseparates it from the first annular ring. Therefore the first step ofthe optimization is to adjust the other geometric parameters until thepressure loss coefficient of this passage is close to the target valuefor the conditioner as a whole. In this particular example, this firststep is achieved by setting the constraint that the circular ligaments99 should be of equal thickness (with the exception of the outer wall,which is fixed at 0.01 D), and then increasing the thickness of those,concurrently reducing the diameter of the central passage, until thedesired loss coefficient is achieved.

The second step is to adjust the width of the radial ligaments 24 ineach ring until the desired velocity profile shape is achieved, whilstalso considering the target for the overall loss coefficient. In thisstep the value for the width of the radial ligaments 24 in each annulusis adjusted iteratively until the desired profile shape and losscoefficient is achieved. The result of this step will be a design whichwill produce the desired velocity profile, and have the intended overallloss coefficient, but may not yet meet some overall requirements such asevery passage having the same hydraulic diameter.

To obtain the same hydraulic diameter for the passages of each ring afurther iterative step involves adjusting the radial width of each ofthe segmented annular channels to satisfy the condition that allhydraulic diameters are the same, keeping all other dimensions constant,with the exception of the diameter of the central passage, which mayalso change. When the adjustment is made in this way, the relativevelocities will diverge again from their target values, requiringfurther iterations to be made.

In the next iterative step, the widths of the circular ligaments 99 areadjusted again to bring the loss coefficient for the central passageback closer to its target value. In the fifth and final iterative stepthe desired velocity profile and loss coefficient is sought, again bymeans of adjusting the width of the radial ligaments 24.

At the end of the five steps described above, the resulting conditionerdesign has an overall porosity of 71% with a calculated loss coefficientof 0.502, a velocity profile within 0.2% of the target, and hydraulicdiameters equal within +/−1.3%. Further steps could be added, but thesewould be unlikely to result in an improved result once manufacturingconsiderations and model limitations are taken into account.

Table 1 shows the geometric parameters of the conditioner that arevaried in this particular optimization example. The values shown in boldas those that were adjusted in each step. Table 2 shows the resultingvalues of hydraulic diameter, pressure loss coefficient and normalizedvelocity for each step. FIGS. 5 a-5 c, 6 a and 6 b illustrate theconvergence of the velocity profile and the hydraulic diametersrespectively. FIG. 7 shows an illustration of the design resulting fromthe optimization example given above. FIG. 8 outlines the optimizationprocess in the form of a simple flow chart.

FIGS. 9 a-9 c show the result of employing a design process similar tothat described to determine the geometry of an optimized conditioner 10design that also accounts for the effects on the passage geometry ofincluding rounded internal corners 40 of a specified radius. FIG. 9 ashows a front view and FIG. 9 b shows a side view. The resultingconditioner design was then manufactured complete with a flange 50 forinstallation between pipe 12 sections, as shown in the photograph ofFIG. 9 c.

The prototype conditioner was tested downstream of a long straight pipe12 and then downstream of an arrangement of six out of plane bends knownto produce asymmetric distortion of the axial velocity profile and togenerate swirl. The tests were conducted using a kerosene substitutefluid with a viscosity of approximately 3 cSt over a range of flowratesin the range of 74 to 740 m3/hr in a 6-inch pipe. A Laws typeconditioner (Nova/CPA 50E variant) was also tested in the sameconfiguration. The arrangement of bends was kept the same for all tests.A meter body with eight ultrasonic flow velocity measuring paths wasused to determine the effectiveness of the flow conditioner 10. The datafrom the eight measurement paths was used in two 4-path combinations todetermine the influence on the hydraulic correction factor of two 4-pathultrasonic flow meters, and all eight paths were combined to give ameasure of the average swirl in the form of a ratio of the tangentialvelocity to the mean axial velocity. The meter factor data for the4-path meters was obtained by calibration in an ISO 17025 accreditedflow laboratory using a unidirectional ball prover as the traceablereference standard. Test data is presented for the followinginstallation combinations:

-   -   Long straight pipe with no flow conditioning    -   Long straight pipe with a Laws type conditioner 10 pipe        diameters upstream of the flow meters    -   Long straight pipe with the new conditioner 10 pipe diameters        upstream of the flow meters    -   Flow meters at 10 pipe diameters downstream of six bends with no        flow conditioning, measurement paths horizontal    -   Flow meters at 10 pipe diameters downstream of six bends with no        flow conditioning, measurement paths vertical    -   Laws type conditioner 4 pipe diameters downstream of six bends,        with the flow meters 10 pipe diameters downstream of the        conditioner    -   New conditioner 4 pipe diameters downstream of six bends, with        the flow meters 10 pipe diameters downstream of the conditioner

FIGS. 10 a and 10 b shows the results for meters A and B in the straightpipe configuration and at 10 diameters downstream of the bends withoutflow conditioning, with the measurement paths in both horizontal andvertical orientations. It can be observed that under these conditions,with no flow conditioning, the swirl and distortion generated by thebends results in changes in meter factor that are typically in the rangeof 0.3 to 0.5%.

FIGS. 11 a and 11 b show the results for meters A and B installed 10diameters downstream of a Laws type thick-plate conditioner. Thedifference between the straight pipe case and the case where theconditioning plate is 4 diameters downstream of the bends is typicallyon the order of 0.1% or less.

These can be summarized quantitatively in terms of a flow weighted meanerror shift. The results of this calculation are given in Table 3.

FIGS. 12 a and 12 b show the results obtained using the new prototypeconditioner previously described. It can be readily observed that thedifference between the straight pipe 12 case and the case where theconditioning plate 16 is 4 diameters downstream of the bends is similarto the case for the Laws type conditioner, typically on the order of0.1% or less. These results can also summarized quantitatively in termsof a flow weighted mean error shift, as reported in Table 3.

The data recorded in Table 3 shows that in terms of the flow measurementperformance of a 4-path ultrasonic meter, the new prototype conditionermatches the performance of the Laws type thick plate 16 conditioner asthe flow weighted mean error shifts are of a similar magnitude, allbeing less than 0.1%.

FIGS. 13 and 14 show the swirl quantified in terms of the tangentialvelocity as a percentage of the mean axial velocity. In FIG. 13, thebare straight pipe 12 case plus the swirl generated by the bends andmeasured ten diameters downstream with no flow conditioning is shown. Itis clear that the bends generate a high level of swirl. FIG. 14 showsthe results for the two flow conditioners tested here, the Laws typeconditioner and the new prototype. Comparing FIGS. 13 and 14 it is clearthat both conditioners substantially reduce swirl. At the higherReynolds numbers it appears that the Laws type conditioner is slightlymore effective at reducing swirl than the new prototype. However, whenthe measurement results of Table 3 are taken into consideration, thisappears to be an insignificant difference.

During these tests, the pressure loss across the prototype conditionerwas measured. The measurements of pressure loss can be converted into adimensionless loss coefficient, which is a useful relative measure ofthe energy lost when flowing through the conditioner. The pressure lossdata is shown in Table 4. For the new prototype, the average losscoefficient is 0.91. This is less than half of the pressure losscorresponding to the Nova/CPA 50E variant of the Laws conditioner, whichhas a loss coefficient of approximately 2.

In conclusion, the results of the tests show that for use with a 4-pathultrasonic meter, the measurement results with the prototype conditionerare equivalent to the Laws type plate 16, but are achieved with lessthan half the pressure loss.

TABLE 1 Width (normalised to pipe diameter) Iteration Outer RadialCircular Middle Radial Circular Inner Radial Circular Centre stepannulus ligament ligament annulus ligament ligament annulus ligamentligament hole 0 0.1200 0.0100 0.0100 0.1200 0.0100 0.0100 0.1200 0.01000.0100 0.2000 1 0.1200 0.0100 0.0205 0.1200 0.0100 0.0205 0.1200 0.01000.0205 0.1370 2 0.1200 0.0443 0.0205 0.1200 0.0211 0.0205 0.1200 0.01880.0205 0.1370 3 0.1040 0.0443 0.0205 0.1302 0.0211 0.0205 0.1278 0.01880.0205 0.1331 4 0.1040 0.0443 0.0202 0.1302 0.0211 0.0202 0.1278 0.01880.0202 0.1350 5 0.1040 0.0425 0.0202 0.1302 0.0240 0.0202 0.1278 0.02080.0202 0.1349

TABLE 2 Normalised hydraulic diameter Loss coefficient Normalisedvelocity Iteration Outer Middle Inner Centre Outer Middle Inner CentreOuter Middle Inner Centre step annulus annulus annulus hole annulusannulus annulus hole annulus annulus annulus hole 0 0.1541 0.1322 0.14000.2000 0.175 0.149 0.138 0.086 0.936 1.015 1.057 1.339 1 0.1541 0.12990.1317 0.1370 0.223 0.269 0.265 0.371 1.050 0.958 0.965 0.815 2 0.14420.1250 0.1279 0.1370 0.620 0.437 0.389 0.371 0.898 1.070 1.134 1.161 30.1331 0.1331 0.1331 0.1331 0.672 0.396 0.365 0.388 0.847 1.103 1.1491.114 4 0.1331 0.1332 0.1334 0.1350 0.669 0.391 0.359 0.371 0.844 1.1041.152 1.134 5 0.1335 0.1317 0.1325 0.1349 0.640 0.443 0.390 0.372 0.8841.063 1.133 1.160

TABLE 3 Flow weighted mean error shift Laws type New thick-plateprototype Meter A 0.08% −0.06% Meter B 0.09% 0.10%

TABLE 4 Differ- Loss ential Differential coefficient, Flowrate Densitypressure Velocity pressure K m3/hr kg/m3 PSI m/s Pascals — 740 800 6.911.3 47574 0.937 607 800 4.5 9.2 31026 0.908 474 800 2.5 7.2 17237 0.827340 800 1.5 5.2 10342 0.965 Average 0.91

Although the invention has been described in detail in the foregoingembodiments for the purpose of illustration, it is to be understood thatsuch detail is solely for that purpose and that variations can be madetherein by those skilled in the art without departing from the spiritand scope of the invention except as it may be described by thefollowing claims.

1. A flow conditioner for a circular pipe having an axis comprising: aplate having a face to be disposed in the circular pipe with the face ofthe plate perpendicular to the axis of the pipe, said plate having acentral circular passage area through which fluid flows surrounded bytwo or more concentric arrays of segmented annular passages for fluidflow defined by separating and subdividing ligaments, with at least onearray of annular passages having a radial width different than a radialwidth of a second array of annular passages.
 2. The flow conditioner ofclaim 1 wherein the plate has at least one subdividing ligament having awidth different than a width of a second subdividing ligament.
 3. Theconditioner of claim 1 whereby the central circular channel issubdivided into 2 or more separate passages.
 4. The conditioner of claim1 whereby the subdivision into segmented annular passages is achieved bymeans of ligaments aligned along a radius of the circular geometry ofthe conditioner.
 5. The conditioner of claim 1 whereby the subdivisioninto segmented annular passages is achieved with ligaments that arealigned at an angle relative to a radius of the circular geometry of theconditioner.
 6. The conditioner of claim 1 whereby the sides of eachsubdividing ligament are straight and parallel.
 7. The conditioner ofclaim 1 whereby the sides of each subdividing ligament are curved. 8.The conditioner of claim 1 whereby the sides of each subdividingligament are non-parallel.
 9. The conditioner of claim 1 whereby theinternal corners of the segmented annular passages are rounded.
 10. Theconditioner of claim 1 whereby the upstream edges of the passages arechamfered or rounded.
 11. The conditioner of claim 1 whereby thedownstream edges of the passages are chamfered or rounded.
 12. Theconditioner of claim 1 whereby all passages have a substantially equalhydraulic diameter.
 13. The conditioner of claim 1 whereby the ratio ofthe length of the passages to their hydraulic diameter is greaterthan
 1. 14. The conditioner of claim 1 whereby the ligaments thatsubdivide the annular passages get progressively thicker at distancesthat are further from the center of the pipe, in order to obtain anapproximation of a fully-developed flow profile.
 15. A flow conditionerfor a circular pipe having an axis comprising: a plate having a face tobe disposed in the circular pipe with the face of the plateperpendicular to the axis of the pipe, said plate having a centralcircular passage area through which fluid flows surrounded by two ormore concentric arrays of segmented annular passages for fluid flowdefined by separating and subdividing ligaments, with at least onesubdividing ligament having a width different than a width of a secondsubdividing ligament.
 16. A flow conditioner for a circular pipe havingan axis comprising: a plate having a face to be disposed in the circularpipe with the face of the plate perpendicular to the axis of the pipe,said plate having a central circular passage area through which fluidflows surrounded by two or more concentric arrays of segmented annularpassages for fluid flow defined by separating and subdividing ligaments,with at least one array of annular passages having a radial widthdifferent than a radial width of a second array of annular passages andat least one subdividing ligament having a width different than a widthof a second subdividing ligament.
 17. A method of producing an optimizedgeometry of flow conditioner for a circular pipe having an axiscomprising the steps of: a. storing a desired value for a pressure losscoefficient of the conditioner in non-transitory memory; b. storing ashape of velocity profile desired in the memory; c. Settingmanufacturing goals; d. storing a number of annular rings to be used inthe conditioner to subdivide the pipe cross-section in the memory; e.storing a number of subdivisions for each annular ring and for a centralcircular passage area of the conditioner in the memory; f. setting awidth of each annular ring to an initial value in the memory; g. settinga width of circular ligaments of the conditioner to an initial value inthe memory; h. setting a width of subdividing ligaments of theconditioner to an initial value in the memory; i. calculating ahydraulic diameter of each of the passages of the conditioner with acomputer from information stored in the memory in steps a-g, thecomputer in communication with the memory; j. setting a thickness of theconditioner plate to a value based on a desired ratio of passage lengthto hydraulic diameter in the memory; k. determining resistance and flowcharacteristics of the conditioner geometry with the computer based onsteps a-g and i; and l. adjusting the geometry iteratively with thecomputer until the goals are achieved.
 18. The method of claim 17including the step of setting a pressure loss coefficient of less than 2in the memory.
 19. The method of claim 17 including the step of enteringinto the memory a target flow profile based on fully developed flowconditions.
 20. The method of claim 17 including the step of enteringinto the memory a flat velocity profile.